Governor



Jan. 16, 1940- J. s. JENNINGS. JR w 2,187,653

GOVERNOR FledJulyS, 1936 2 Sheets-Sheet l INVENTOR Mams-f1 Jan. 16, 1940. J. s. JENNlNc-zs. JR

GOVERNOR Filed July 9, 1936 2 Sheets-Sheet 2 om' lhl hw.. s u l. MW, QM, b QN. hm.. Qn. hw. QN. .mi Q; h6. .0..\ Q S///H/// N /l 9m /l /l nu TQ Q uw .Mmmmuw all) Patented Jan. 16, 1940 GOVERNOR Jarvis S. Jennings, Jr.

to Monarch Governor Company,

, Detroit, Mich., assigner Detroit,

Mich., a corporation of Michigan Application July 9, r1936, Serial No. 89,807

19 Claims.

This invention relates to governors for internal combustion engines,` such as governors of the vacuum or suction or so-called velocity types utilizing a governing Valve such as va valve of the butterfly type, either balanced or unbalanced, mounted in the intake passage between the carburetor and engine manifold.

An` object of the invention is to provide an' improved governor of the foregoing type which is relatively ysimple and compact in construction, economical to manufacture, and capable of governing relatively accurately under varying loads not only at a given` speed but also at different set speeds for which the governor is adjusted.

'A further object is to provide a suction or vacuum operated governor having improved controlling mechanism interposed between the valve and `counteracting spring whereby the effort of the suction or vacuum responsive member Will be counterbalanced in all positions thereof when the governor is set or adjusted at different speeds.

A further object is to provide a governor having a governing butterfly valve movable toward closed position by the operation of the engine, a spring being provided for `opposing the closing of the valve, and wherein improved jointed linkage is interposed between the valve shaft crank arm and the spring, the relative' angularity of the linkage being controlled by a cam.

Other objects of this invention will appear in the following description and vappended claims, reference being had to the accompanying drawings formng a part of this specification wherein like reference characters designate corresponding parts in the several views.

Fig. l is a side View, partly in section, illustrating a governor embodying the present invention installed in the intake passage of an internal combustion engine.

Fig. 2 is a horizontal section taken through lines 2--2 of Fig. l in the direction of the arrows.

Fig. 3 is a diagram illustrating typical vacuum curves adapted to be generated by a governor valve controlled in accordance with the present invention.

Fig. 4 is a fragmentary side elevation of the governor embodying certain modifications.

Fig. 5 is a View similar to Fig. 4 illustrating further modifications.

Before explaining in detail the present invention it is to be understood that the invention is not limited in its application to the details of construction and arrangement of parts illustrated in the accompanying drawings, since the invention is capable of other embodiments and of being practiced or carried out in various ways.

Also

it is to be understood that the phraseology or terminology employed herein is for the purpose of description and not of limitation, and it is not intended to limit the invention claimed herein 5 beyond the requirements of the prior art.

In the drawings there is illustrated, by way of example, a governor comprising a governor body 'IU adapted to be installed in the intake passage leading from the carburetor to the intake manifold of an internal combustion engine.

In the ception of bolts I2 by means of which it may be4 secured to the flange I3 of the intake pipe I4. Since the governor body IU is interposed in the intake pipe leading to the intake manifold, its passage therethrough forms a portion of the intake passage from the carburetor to the manifold. Installed inthe portion I4 of the intake pipe above or at the carburetor side of the governor is a suitable carburetor throttle valve II of the but.

terfly type fastened to a cross-shaft I 6 rotatable in suitable bearings to permit angular movement of the valve, this valve being manually operated in well known manner.

Centered within the passage I 5 of the governor body I0 is a governing valve I8 which in the present instance is shown as of the butterfly type and preferably, although not necessarily, substantially balanced with respect to the cross-shaft I9 to which the governingvalve is secured. The governing valve shaft I9 is journalled at one end in suitable bearings within the boss Ia of the Valve body. The opposite end ISa of the shaft projects through the wall of the body I0 into the interior of a casing 20 offset to one side of the governor body, this end ISa of the valve shaft being journalled in suitable bearings in the wall of the body. The casing 20 is accessible from the outside through a rectangular opening at one side thereof which is closed by means of a suitable cover plate 2I held in place by suitable screws. The casing 20 has a generally cylindrical or barrel-like extension 22 provided longitudinally thereof with an annular or cylindrical bore 22a closed at its outer end by means of a removable cap 23 held in place by screws 24.

Within the to slide in the cylinder.

This piston at its outer end has a central recess 26 forming a socket to receive and hold one end of a compression spring 21. The opposite end of the spring bears against and is held in position by means of a spring retainer 28 which is tapped to receive an adjusting screw 29. The screw is accessible at 30 for rotation to permit adjustment of the retainer collar 28 and thereby adjustment of the tension of the spring 21,

'I'he piston 25 is fitted with a transverse pin 3l to which are pivotally connected a pair of spaced.

parallel links 32 extending into a centrally located bore 33 in the inner side of the piston and held in properly spaced relation. against the opposite walls of the recess 33 by a spacer Sla'on the pin 3l. The links 32 are pivotally connected at their opposite ends to a hinge pin 34 and also pivotally connected to this pin are a pair of spaced parallel links 35 held in suitably spaced relation as shown in Fig. 2. The links 35 form in conjunction with the links 32 a two-part jointed connecting rod in which the parts are hinged together at 34 for relative angular movement. The links 35 at their ends opposite the hinge pin 34 are held in spaced relation by means of a tubular spacer 36 and are pivotally connected to a pin 31 which yis fastened to the outer end of a crank arm 38 fixed to the end lila of the governf ing valve shaft 18. In the embodiments illustrated in Figs. 1 to 5 inclusive the opposite end of the crank armis extended somewhat beyond the Valve shaft and enlarged to provide a counter-weight 39.

Rotatably mounted upon the hinge pin 34 between the links 35 and held in spaced relation therefrom is a cam roller 40 adapted to engage and travel over the curved cam surface 4|c1l of a cam block or member 4I. The latter is supported within the casing 20 directly beneath the connecting rod links 32 and 35 and extends longitudinally in a direction parallel thereto. The cam member 4l is mounted preferably in such manner as to provide for a compound adjustment thereof, that is, an adjustment vertically with respect to the cam roller 40 and an adjustment longitudinally or in an endwise direction. In the illustrated example the cam 4I may be adjusted vertically or endwise or both so as to properly position the cam surface 41a in order to accommodate or provide for different speed adjustments. The means for adjusting the cam 4I in the present instance, by way of example, takes the form of a pair of adjusting screws 42 threaded into tapped holes in the bottom of the cam block at opposite ends thereof, the Shanks of the screws passing through elongated slots in the bottom of the casing 20, as shown in dotted lines, to permit longitudinal movement when the cam block is adjusted endwise. Threaded into a tapped hole in one end of the cam block is an adjusting screw 43, in like manner passing through a vertically elongated hole or slot 43a in the side w'all of the casing, Thus, by means of the Screws 42 the cam block 4d may be moved upwards or downwardly and by means of the adjusting screw 43 the cam block may be moved or adjusted endwise. A compound adjustment of the block, i. e., in two directions, may be aecomplished by adjusting all three screws.

In some types of governors it is found unnecessary to incorporate any additional mechanism in order to maintain the cam roller 40 in constant engagement with the cam surface 4|a. For instance, if the direction of rotation of the gover- Vof to a light spring 41.

nor valve is opposite to that of the carburetor valve I1 the roller 40 will ordinarily follow the cam 41a without the aid of any greater force than the weight of the roller and linkage 32, 35.

It will be understood that with the carburetor 5 valve wide open there is always a closing tendency on the governing butterfly valve even when the latter is geometrically balanced, and hence this effort or effect supplemented by the weight of the roller and linkage will in many instances 10 maintain the roller in contact with the cam at all times except perhaps when the carburetor valve is closed to a greater degree than is necessary for the governing valve to close in order to maintain the desired speed. In some instances, parl5 ticularly when the direction of rotation of the two valves is the same, the roller 40 will not under all conditions follow the cam when the Carburetor valve is partially closed.

Alternative methods of'ensuring constant con- 20 tact of the cam roller with the cam are shown in Figs. 4 and 5. As illustrated in Fig. 4, the links. 32 and 35 are provided with bell crank arms 45 and 46 extending upward in a direction such as to lprovide a suitable'space between the extremities of the bell cranks for connection there- This spring need have only suflicient tension to resist the countertorque of the valve set; up by eddy currents from the carburetor'valve when it is partially closed. 3G The construction of the governor embodying the modification of Fig. 4 may otherwise be the same as that above described. With reference to Fig.

5, it will be seen that there is substituted for the r cam block 4l a cam plate or block 48 mounted in 35 the same manner but provided with a cam slot 49 having upper and lower cam surfaces 49a of similar contour and curvature. In this instance, the cam roller 40 travels within the cam slot 49 engaging uniformly opposite faces thereof with the links 35 and 32 straddling opposite sides of the cam plate 48. With the foregoing modifications the governor of Fig. 5 may otherwise be constructed as illustrated in Figs. 1 and 2. The double or slotted cam of the form shown in Fig. 5 45 is preferred for many types of governors inasmuch as the bearing loads on the connecting rod links 32 and 35 are reduced when they are not subjected to any spring tension and accordingly the friction lag, which it is desirable to avoid in a governor, is substantially eliminated.

`The crank arm 38 of the governing valve shaft is preferably provided with the counter-weight 39 which provides a sufiicient closing'force to substantially balance the weight of the valve shaft 56 crank arm 38 andy thatportion of the linkage which exerts in theopen position of the valve a force opposed to the normal closing effort on the valve. This counter-weight is so positioned as to exert its maximum closing force or effort 60 at the time when the governing valve is in its wide open position.

Heretofore, it has been impossible to make a practicable commercial governor of the vacuum or suction, so-called velocity type, which will give equally efficient performance at both high and low speeds as Well medium or intermediate speeds. This has been due largely to the fact that the character of the vacuum curve generated by a governing butterfly valve rotating in a conventional throttle or intake passage has markedly different characteristics at different speeds. The general practice in the attempt to attain a wide range of adjustment has been to sacrice power when the governor is adjusted to its lowest speed and to sacrifice accuracy of performance in the light load ranges when the governor is adjusted for its maximum speed. Even under these conditions it has been difficult to secure the desired range without reaching the critical point where the governor is insuiliciently stabilized against surging or hunting.

In the present instance, these disadvantages have been overcome and it is possible by virtue of the present invention to secure a wide range of adjustment without sacrificing either full power or accuracy of performance. One of the important features of the illustrated governor by reason of which these results are attained resides in the fact that a mechanism is utilized whose characteristics change in the same general way as the character of the vacuum curves at various speeds, such for example as the curves plotted in Fig. 3. In the diagrams illustrated in this figure A indicates a typical high speed curve, B` a typical medium or intermediate speed curve, and C a typical low speed curve.r In each instance, as is necessary in order to substantially balance the vacuum or suction forces and the effort of a straight line spring, the governing valve has a disproportionately greater angular movement as compared with the spring deflection or `movement near the open end of the valve travel than near its closed end, or stated in another way, for each given increment of angular movement of the valve the spring will have a disproportionately greater movement or deflection near the closed or no load position of the valve than near `its open. or full load position. It will be seen with reference to Fig. 3 that as the governor is adjusted from high to low speed the degree of disproportion between the relative spring or piston and valve movements increases markedly. For instance, for a given increment of piston travel or spring deflection near the open end the valve has a markedly greater angular movement at the low speed adjustment than at high speed. Moreover, at the closed (no load) end the valve has a substantially less an,- gular movement for a given increment of piston travel or spring deflection at the low speed adjustment than at high speed. Thus, as seen from Fig. 3, as the speed increases the more nearly the vacuum curve approaches the straight line deflection curve of the spring, the curve A being considerably flatter or more nearly straight than the curve C. In accordance with the present invention the preferred mechanism for accomplishing this, including the cam 4|, its adjusting i means, and the angularly related links 32 and 35,

is such as to substantially produce these variable characteristics simply by adjustment of the mechanism since the latter when adjusted varies substantially in accordance with the Variations in the curve characteristics.

. The contour of the cam face Mais so developed that in cooperation with the changing angularity of the links 32 and 35 it will in conjunction with the angular motion of the crank arm 38 accomplish the foregoing purposes. It will be seen that when the cam is adjusted upward for higher speeds it tends by changing the relative angularity of the links 32 and 35 to increase the effective spring tension and, also, by reducing the angle between links 32 and 35 it produces a reduction in the rate of travel of the piston, or the rate of spring deflection, with respect to the angular movement of the crank arm or valve shaft near the closed end of the valve, as seen, for example, by comparing curve C with curve B or curve A. In effecting the adjustment from a lower to a higher speed it is desirable that the forward or right hand end of the cam. as seen in Fig. 1, be raised at a somewhat greater rate than the opposite or no load end.

In the illustrated example the form of linkage 32 and 35 is such that in the low speed adjustment the shape of the cam face 4|a is generally parabolic or in which it has a curve of diminishing radius at the open or full load end of the valve travel. In adjusting the governor for higher speeds the cam 4| is adjusted upward and forwardly so that the roller 40 is caused to travel on a curve of generally greater radius.

I claim:

l. In a governor for an internal combustion engine having an intake passage, a governing valve in said passage movable toward closed position by the operation of the engine, spring means opposing said movement, a valve shaft having a crank arm for turning the valve, a pair of jointed devices interposed between the spring and crank arm, and a cam cooperating with said devices at their joint for controlling the relative angularity thereof during the movement of the valve.

2. In a governor for an internal combustion engine having an intake passage, a governing valve in said passage movable toward closed position by the operation of the engine, spring means opposing said movement, a valve shaft having a crank arm for turning the valve, jointed members interposed between the spring and crank arm, a cam cooperating with` said members for controlling the relative angularity thereof during the movement of the valve, and means for varying the position of said cam relatively to said spring means.

3. In a governor for an internal combustion engine having an intake passage, a governing valve in said passage movable toward closed position by the operation of the engine, spring means opposing said movement, a valve shaft having a crank arm for turning the valve, jointed members interposed between the spring and crank arm, a normally stationary cam cooperating with said members for controlling the relative angularity thereof during the movement of the valve, and means for adjusting said cam in different directions.

4. In a governor for an internal combustion engine having an intake passage, a governing valve in said passage, a vacuum responsive piston for moving said valve toward closed position, spring means opposing said movement, a valve shaft having a crank arm for turning the valve, an operative connection between the piston and said crank arm comprising angularly related jointed members, and means for changing the angularity of said members during the travel of the piston.

5. In a governor for an internal combustion engine having an intake passage, a governing valve in said passage, a vacuum responsive piston for moving said valve toward closed position, spring means opposing said movement, a valve shaft having a crank arm for turning the valve, an operative connection between the piston and said crank arm comprising a pair of angularly related members pivoted one to the other, and a cam cooperating with said members at the pivot thereof for varying the relative angularity of said members.

6. In a governor for an internal combustion engine having an intake passage, a governing valve in said passage, a vacuum responsive piston for moving said valve toward closed position,- spring means opposing said movement, a valve shaft having a crank arm for turning the valve,

, an operative connection between the piston and said crank arm comprising a pair of angularly related members pivotedone vto the other, cam meansl cooperating with said pivoted members for varying their relativesingularity-and means for adjusting the position of said cam means relatively to the spring-means.

A'7. In a governor for an internal combustion engine having an intake passage, a governing buttery valve in said passage, a vacuum responsive piston for moving said valve between closed and open positions thereof, spring means opposing said movement, a crank arm for turning said valve, angularly related vmembers pivoted one to. the other connecting said-piston and crank arm,

, and a camv cooperatingwith said pivoted membersifor varying their relative angularity during operationof the governor, said governor having provision for compound adjustment of said cam.

8. In a governor for an internal combustionl lengine having an intake passage, a governing valve in said passage movable betweenopen and closed positions by the operation of the engine, a spring opposing said movement, means between the-spring and valvefor. producing 'at a given speed setting a disproportionately greater angular movement of the valve as compared with the movement of the spring near the open position of the valve than near the closed position. and means independent of the spring for adjusting the governor for operation at a different set speed and effective to vary the degree of said disproportion between said spring and valve movements. i n

9. In a governor for an internal combustion engine having an intake passage, a governing valve in said passage movable between open and closed positions by the operation of the engine, a spring opposing said movement, means between the spring and valve for producing at a given low speed setting oi the governor a disproportionately greater angular movement of the valve as compared with the movement of the spring near the open position of the-valve than near the closed position, and means independent of the spring for adjusting the governor for operation at ahigher set speed and effective to decrease the degree oi: disproportion between said spring and valve movements.

l0. In a governor for an internal combustion engine having an intake passage, a governing valve in said passage, a vacuum operated piston for moving ysaid valve between open and closed positions, a spring opposing said movement, means between the piston and valve and includ-- ing a jointed connecting rod yfor producing at a given low speed setting a disproportionately greater angular movement of the valve as compared with the movement of the piston near the open position of the valve than near the closed position, and means independent of the spring for adjusting the governor for operation at a higher set speed and effective to decrease the degree of said disproportion between said piston and valve movements. v

11. In a governor for an internal combustion engine having an intake passage, a governing valve in said passage, a vacuum. operated piston for moving said valve between open and closed positions, a spring opposing said movement, a ycrank arm connected to said valve, means comprising apair of jointed members connecting the piston and crank arm and an adjustable cam cooperating with said members for producing at a given speed setting a disproportionately greater angular movement of the valve as compared with the movement of the piston near the open position of the valve than near the closed position, and means for adjusting the governer for operation at adifferent set speed and eiective to vary the degree of said disproportion between said piston and valve movements.

12. In a governor for an internal combustion engine having an intake passage, a governing valve in said passage, a vacuum operated piston for moving said valve between open and closed positions, a spring opposing said movement, a crank arm connected to said valve, means comprising a pair of jointed members connecting the piston and crank arm and an adjustable cam cooperating With said members for producing at a given low speed setting a disproportionately greater angular movement of the valve as compared with the movement of the piston near the open position of the valve than near the closed position, and means for adjusting the governor for operation at a higher set speed and effective to decrease the degree of said disproportion between said piston and valve movements.

13. In a governor for an internal combustion engine having an intake passage, a governing valve in said passage, a vacuum responsive member for moving said valve between open and closed positions, a spring opposing said movement, a valve shaft having a crank arm, an articulated jointed connection between said crank arm and piston, a cam roller carried by said jointed connection, and an adjustable cam engaged by said roller and so constructed that adjustment of the cam for an increased speed setting of the governor is effective to reduce the relative angularity of the parts of said jointed connection.

'14. In a governor for an internal combustion engine having an intake passage, a governing valve in said passage, a vacuum. responsive member for moving said valve between open and closed positions, a spring opposing said. movement, a valve shaft having a crank arm, an articulated jointed connection between said crank arm and piston, a cam roller carried by said jointed connection at the joint thereof, and an adjustable cam engaged by said roller and so constructed that adjustment of the cam for an increased speed setting of the governor is effective to reduce the relative angularity of the parts of said jointed connection.

15. A governor for an internal combustion engine havingan intake passage, a governing valve in said passage, a vacuum operated member for moving said valve between open and closed positions, a spring opposing said movement, a valve shaft connected to said valve and having a crank arm, and adjustable means connecting said arm and member and eiective to produce a condition of substantial balance between the vacuum force acting on said member and the opposing effort of the spring at all positions of the valve at each of several predetermined speed settings of the governor.

16. A governor for an internal combustion engine having an intake passage, a governing valve in said passage, a vacuum operated member for moving said valve between open and closed positions, a spring opposing said movement, a valve shaft connected to said valve and having a crank members, one pivotally connected to said member and the other pivotally connected to said arm, and an adjustable cam cooperating with said members to vary their relative angularty.

17. In a governor for an internal combustion engine having an intake passage, a governing valve in said passage movable toward closed position by the operation of the engine, spring means opposing said movement, a valve shaft having a crank arm for turning the valve, a pair of articulated members connected together end to end, one of said members being pivotally connected to said crank arm, a roller associated with said members, a normally stationary contoured cam cooperable with said roller, and manually operable means to adjust said cam relative to said roller.

18. In a governor for an internal combustion engine having an intake passage, a governing valve in said passage movable toward said closed position by the operation of the engine, a valve shaft, a pair of jointed members pivotally connected at adjacent ends, the opposite end of one of said members being connected to the valve shaft, spring means exerting an effort on the oppcsiteend of the other of said members, an antifriction device associated with said jointed members intermediate the opposite ends thereof,

a cam cooperating with said antfriction device,

and manually operable means to vary the position of the cam relative to said antifriction device.

19. In a governor for an internal combustion engine having an intake passage, a butterfly governing valve in said passage movable toward closed position by operation of the engine, spring means opposing the closing movement or" said valve, a pair of jointed members interposed between the spring and valve, a roller associated with the jointed members, a normally stationary cam engaging the roller, and means for adjusting the cam relative to the roller.

JARVIS S. JENNINGS, JR. 

